Accumulator with tens transfer means disposed internally of its pinion-bearing shaft

ABSTRACT

An accumulator comprising a plurality of ordinal pinions rotatably supported on a hollow shaft is provided with tens transfer means disposed within the shaft. Carry pawls protruding through apertures in the shaft are depressibly indexed by their associated pinions as the latter are rotated past their full capacity positions. Means are provided for rotating the shaft a predetermined distance in a counteraccumulating direction, and then in an accumulating direction, relative to the pinions. Means within the shaft are activated subsequent to such counteraccumulating rotation to rockably incline the indexed pawls into coupled relationship with their adjoining higher order pinions, such coupled relationship being effective to advance the latter pinions a one-unit distance as the shaft is rotated in the accumulating direction following its predetermined counteraccumulating rotation.

United States Patent [72] Inventors Bernard Deleuze;

Pierre Leonard Dugeny, both of Paris; Jean Rene Gerain, Pantin; Jacques Michel Queffeleant, Fraconville, all of, France [21] Appl. No. 762,165

(22] Filed Sept. 16,1968

[45] Patented June 1,1971

[7 3] Assignee Burroughs Corporation Detroit, Mich.

[541 ACCUMULATOR WITH TENS TRANSFER MEANS DISPOSED INTERNALLY OF ITS PINION- Primary Examiner-Richard B. Wilkinson Attorneys-Kenneth L. Miller and Frank H. Cullen ABSTRACT: An accumulator comprising a plurality of ordinal pinions rotatably supported on a hollow shaft is provided with tens transfer means disposed within the shaft. Carry pawls protruding through apertures in the shaft are depressibly indexed by their associated pinions as the latter are rotated past their full capacity positions. Means are provided for rotating the shaft a predetermined distance in a counteraccumulating direction, and then in an accumulating direction, relative to the pinions. Means within the shaft are activated subsequent to such counteraccumulating rotation to rockably incline the indexed pawls into coupled relationship with their adjoining higher order pinions, such coupled relationship being effective to advance the latter pinions a oneunit distance as the shaft is rotated in the accumulating direction following its predetermined counteraccumulating rotation.

PATENTEB Jun nan SHEET 1 0F 9 INVENTORS. BERNARD DELEUZE. PIERRE L. 0065M. JEAN R GERA/N JACOUES M. 'OUEFFELEANT.

AGENI PAIENTEU Jun new SHEET 2 OF 9 PATEVVNTEDJUN usn 358L983 SHEET 3 [IF 9 FIG.6.

PATENTEU'JHN H971 3,581,983

' man 5 OF 9 PATENTEnJuN 1 I97! SHEET 8 UF 9 FIG.II."-

Fla/2Q ,PATENTEDJUM l|97| 3,681,983

- same or 9 'IIII/III /I/IIIIIIII BACKGROUND OF THE INVENTION Accumulators used in calculators and other business machines generally comprise a plurality of gears or pinions which are rotationally advanced according to the digit values of the amounts accumulated. Such accumulators areprovided with transfer means effective for advancing the adjoining. higher order pinion a one-unit distance when a given lower order pinion is rotationally advanced past its full capacity position. In a decimal accumulator, for example, the advancement of pinions past their nine positions will result in the introduction of a value of one into the adjoining higher order pinions, and the accumulation of a value of one in the units order of an accumulator all of the pinions of which have been advanced to their nine positions will result in the successive transfer of a value of one into each higher order pinion such successive transfer being commonly referred to as a runthrough carry.

A variety of tens transfer devices are known and have been employed in connection with such accumulators to accomplish this one-unit advancement of the higher order pinions upon the occasion of an exceed capacity conditiondeveloping in the adjoining lower order pinions. In addition to the varia- .tions in design and structure that have emanated from sundry inventive concepts, other variations have been influenced by the location of such accumulators within the calculating or business machine and by the presence of conflicting mechanisms in such locations.

Tens transfer devices commonly comprise a plurality of carry pawls and a plurality of associated carry racks or drivers, the carry pawls being conditioned by the rotation of their associated pinions, when the pinions are engaged with the add racks, to activate their associated carry drivers when the pinions are disengaged from the add racks, such activation .of the carry drivers being effective to advance the adjoining higher order pinions a one-tooth or one-unit distance. Common characteristics of these known tens transfer devicesare the placement of the carry pawls and carry drivers in an area contiguous to and outwardly disposed of the periphery of:the

pinions, and the use of resilient means for sequentially activating the carry drivers to advance the adjoining higher order pinions. These known devices have accordingly been marked by limitations to space conservation, and by limitations in'the number of accumulators that can be employed in calculators and business machines of predetermined size and shape. Consistent reliance upon spring means for advancing the higher order pinions has also presented limitations in reliability,.and has tended to restrictively influence the periods of troublefree performance.

SUMMARY OF THE INVENTION It is accordingly an object of the present invention to provide a compact and space saving accumulator. which may be used in multiple combinations in calculators and business machines with a minimum concession to bulk and weight. It is also an object of the present invention to provide an accumulator that includes a highly reliable tens transfer device wherein the tens transfer function is performed by positive .and nonresilient means.

It is a further object of the present invention to provide an accumulator that is simple in design and comprises a minimum number of parts.

An important aspect of the invention is the use of depressiblc and rockably inclinable carry pawls which are endanchored within a hollow shaft that provides rotational support for the accumulating pinions. These pawls are depressible to an intermediate indexed position by the rotation of their associated pinions from their respective nine to zero positions, and depressible to a fully indexed position by a predetermined rotation of the pinion-bearing shaft relative to the pinions.

Another aspectofthe invention is the use of slidable means disposed within the hollow pinion-bearing shaft, such means being translatably activated at a predetermined point in an accumulating operation to effectively incline those pawls which are located in their fully indexed positions, and to also incline those pawls which are located in their intermediate indexed positions and which at the same time leftwardly adjoin either a fully indexed pawl or one or, more intermediately indexed pawls which leftwardly adjoin a fully indexed pawl. This inclining of the. intermediately indexed and fully indexed pawls is effective to couple such pawls with projections formed on their respective-higherorder pinions.

Still another aspectof the invention is shaft-rotating means effective for rotating the hollow pinion-bearing shaft a predetermined reciprocal distance relative to the pinions. An initial rotation of the shaft in a countcraccumulating direction occurs prior to the translation ofthe slidable means and is effective to fully index those pawls which were depressibly activated to their intermediate positions by the rotation of their associated pinions, and effective also to intermediately index those pawls which are associated with pinions that are disposed in their full-capacity positions. A'succeeding rotation of the hollow shaft in an accumulating direction occurs subsequentto the translation of the slidable means, and is effectiveto advance the pinions with which the inclined pawls are coupled a one-unit distance in the accumulating direction.

BRIEF DESCRIPTION OF THE DRAWINGS These and other objects, aspects and advantages of the invention will be more clearly understood from the following description when read in conjunction with the accompanying drawings, in which:

FIG. I is a perspective viewof the preferred embodiment of the invention taken from the left front corner of a calculating machine in which it isincorporated and showing the accumulating pinions in rclationto the various control and actuating means;

FIG. lAis a perspective view showingthe additive relationship of control cams and a pair of projections of a translatable shaft, such cams and projections serving to control the rotation of the pinion-bearing shaft relative 'to the pinions during additiveand subtractive accumulating operations;

FIG. 1B is a perspective view showing the alignment of the cams and projections ofFIG. IA for a subtractive accumulating operation;

FIG. 1C is a side view of one of the movable frame members providing support:for the pinion-bearing shaft of the invention and wherein the, details of a pair of activating cams are illustrated;

FIG 2 is a cutawayview showingsome of the pinions and pawls and the hollow pinion-bearing shaft with means disposed within the shaft for rockably inclining the pawls that are depressibly indexed;

FIG. 2A is a view similar to that of FIG. 2 and showing a fully indexed pawl and a partially indexed pawl in their rockably inclined and coupled positions relative to their higher order pinions,-and showingalso an upright pawl that" has been neither depressible indexed nor rockably inclined,

the various aligned relationships of the projections 45B of the pawls with the slide partitions 43 and the interposers 47 also being shown;

FIG. 3 is aperspective view taken from the left side of the accumulator and showing a single pinion in relation to the hollow shaft and to the pawl with which it is indexibly associated;

FIG. 4 is a perspective view taken from the right side of the FIG. 6 is a right-side view of an accumulating pinion showing the notches or slots formed on the toothed portion thereof with which the pawl indexibly associated with the adjoining lower order pinion is coupable;

FIG. 7 is a left-side view of an accumulating pinion together with a cross-sectional view of the hollow pinion-bearing shaft and the slidable means disposed therewithin, the relationship of the pawl to the wedge-shaped camming surface of the pinion representing the plug zero and minus nine positions of the pinion;

FIG. 8 is a left-side view of the pinion and shaft of FIG. 7 with the pawl so oriented as to represent the plus one and minus eight positions ofthe pinion FIG. 9 is a left-side view of the pinion and shaft of FIG. 7 with the pawl disposed in its intermediately depressed position, the pinion having been advanced from its plus nine to its plus zero position;

FIG. 10 is a left-side view of the pinion and shaft of FIG. 7 with the shaft and pawl disposed in their initial rotated positions relative to the pinion and with the pawl disposed in its fully indexed position as a result of the action of an angular camming surface of the pinion on a stud of the pawl during such rotation of the shaft and pawl;

FIG. 11 is a left-side view of the pinion and shaft of FIG. 7 with the shaft and pawl disposed in their initial rotated positions relative to the pinion and with the pawl disposed in its intermediately depressed position as a result of the action of the wedge-shaped camming surface of the pinion on the pawl during such rotation ofthe shaft and pawl;

FIG. 12 is a left-side view of the pinion and shaft of FIG. 7 with the shaft disposed in its home position after its return rotation relative to the pinion and with the pawl disposed in its intermediately depressed and inclined positions; and

FIG. 13 is a sectional elevation of a calculating machine schematically showing the preferred embodiment of the invention in relation to rotary means for additively and subtractively advancing the accumulating pinions.

DETAILED DESCRIPTION OF THE INVENTION With reference to FIG. 1, the preferred embodiment of the invention comprises a plurality of accumulating pinions 21 which are rotatably supported on a hollow shaft 23, the shaft in turn being rotatably supported by a pair of movable frame members 29 which are rotatably and translatably disposed between machine frame members 35 and 36. As shown in FIG. 4, the pinions 21 are held in their respective positions on the shaft 23 by means of clips 25 which are locked to the shaft by means of detenting projections formed in the clips and indentions formed in the shaft. A plurality of apertures 27 formed in the shaft 23 provide for the accommodation of a plurality of pawls 45 which are depressibly activated by their respective pinions 21 and rockably activated by means to be described hereinafter.

Each of the accumulating pinions 21 comprises a toothed portion 21A and a ring portion 218 as shown in FIGS. and 6. The toothed portions 21A are rotatably activatable by suitable accumulating actuators in the process of additively and subtractively entering amounts therein, and a plurality of projections 21E and 21F formed on the left-side and right-side surfaces thereof, respectively, provide for the depressible activa tion of the associated pawls 45, and for the coupling of each pinion with its rightwardly adjoining pawl 45 when the latter pawl has been rockably inclined, respectively, as will be explained in a subsequent section. The ring portions 218 are provided with projections 21C (FIG. 2) which serve as zero locators when they are brought into contact with a total stop bail (not shown) during a total-taking operatio and provided also with wedge-shaped camming surfaces 21D (FIG. 5) which in relation to the pawls 45 serve to denote the relative positions of the pinions and which are effective to depressibly activate the pawls 45 to their intermediate positions when the pinions are. rotated past their nine positions to their zero positions. FIGS. 7 and 8 show a pinion in its plus zero and plus one positions, respectively, and FIG. 9 shows a pinion with its pawl located in the intermediate position. The projections 21E formed on the left-side surfaces of the pinions 21 serve as angular camming surfaces which cooperate with corresponding studs 45A (FIG. 2) disposed on the right-side surfaces of the pawls 45 to depressibly activate the pawls to their fully indexed positions, as hereinafter described in greater detail. A plurality of projections 216 (FIG. 5) disposed in spaced-apart relationship on the left-side surface of each ofthe toothed portions 21A provide a circular groove for the accommodation of the stud 45A of the associated pawl 45 when the pinion is rotated with the pawl located in its uppermost position, such spaced-apart relationship of these projections providing a series of radially oriented grooves for the accommodation of the stud 45A as the pawl 45 is restored upwardly to its uppermost position following the completion ofa tens transfer operation. The plurality of projections 21F (FIG. 6) disposed in spacedapart relationship on the right-side surface of each pinion 21 provide a coupling facility as between such pinion and its rightwardly adjoining pawl when the pawl is rockably inclined, as illustrated in FIGS. 2A and 4 and as hereinafter described.

The movable frame members 29 are rotatably and translatably activatable on the sleeve 55 as shown in FIG. 1, such sleeve being journaled within the machine frame members 35 and 36, to thereby activate the accumulating pinions 21 into and out of engagement with the accumulating actuators 113 or 115. When disengaged from the accumulating actuators, the pinions 21 are moved into contacting relationship with fingers springs 39 (FIG. 2) formed on a detent bail 37 which is fixed to a support member 97 (FIG. 1) anchored to the machine frame members 35 and 36.

Disposed within the shaft 23, as best seen in FIGS. 2 and 2A, are means for rockably inclining those pawls 45 which have been depressibly activated to their fully indexed positions by one of the pair of angular camming surfaces 21E of their respective pinions, and for rockably inclining also those pawls which leftwardly adjoining a fully indexed pawl and which have themselves been depressibly activated to their intermediate positions by the wedge-shaped camming surface 21D of their respective pinions. Such means disposed within the shaft 23 comprise an internal shaft 41 extending outwardly from the right end of the sleeve 23 and having a plurality of slopes 41A formed in a portion thereof corresponding to the placement of the pinions 21 on the sleeve 23, an indexing slide 43 having a plurality of rectangular apertures, an apertured anchor strip 49 into the apertures of which the pawls 45 are rockably and translatably fitted, an automatic one slide 51 translatably disposed between the shaft 41 and the slide 43, and a plurality of interposers 47 which are floatably disposed within the rectangular apertures of the indexing slide 43 between adjoining pairs of pawls 45. The interposers 47 are each provided with an enlarged upper portion which is maintained in contacting relationship with the upper surface of the indexing slide 43, and with a lower reduced portion which extends downwardly a minimal distance into a rectangular aperture of the indexing slide between a partition of such slide and a pawl jointly housed within such aperture. At a predetermined point in a tens transfer operation, as will be explained in greater detail hereinafter, the internal shaft 41 and the indexing slide 43 are translated a predetermined distance to the left, and, at a later point in such operation, are translated an equivalent distance in a return direction.

Each of the pawls 45 is provided on its right-side surface with the previously mentioned stud 45A which cooperates with the angular camming surfaces 21E of its corresponding pinion, and a projection 458 (FIG. 2A) which is horizontally aligned with the rightwardly adjoining partition of the indexing slide 43 when the pawl is located in its fully indexed position, and horizontally aligned with the rightwardly adjoining interposer 47 when the pawl is located in its intermediate position. These horizontal aligned relationships are best shown in FIG. 2A. The leftward translation of the indexing slide 43 will accordingly serve to rockably incline those pawls which are located in their fully indexed positions, through contact of the partitions of the indexing slide with the projections 45B of such fully indexed pawls. When a given pawl is rockably inclined by means of such contact of a partition of the indexing slide with its projection 458, the leftwardly adjoining interposer 47 jointly housed in an aperture of the slide with the inclined pawl is translated a predetermined minimal distance to the left within such aperture. Should such translation of the jointly housed interposer effectuate contact with the projection 45B of the adjacent higher order pawl (as also shown in FIG. 2A), such pawl having been depressibly activated to its intermediate position, the latter pawl will also be rockably inclined, to thereby effectuate a corresponding minimal leftward translation of the interposer jointly housed therewith, and to rockably incline the next higher order pawl in the event it, too, is disposed in its intermediately depressed position. Should the leftward translation of an interposer not effectuate contact with the projection 45B of the adjacent higher order pawl, however, such pawl not having been depressibly activated, the adjacent higher order pawl will not be rockably inclined but will remain in its upright position, as illustrated by the leftmost pawl in H0. 2A. 1t can therefore be seen that the leftward translation of the indexing slide 43 is effective to rockably incline those pawls 45 which have been depressibly activated to their fully indexed positions by the action of the angular camming surfaces 21E of their associated pinions 21, and effective also to rockably incline those pawls which leftwardly adjoin a fully indexed pawl and which in turn have been depressibly activated to their intermediate positions by the wedge-shaped camming surfaces 21D of their associated pinions. Whether resulting directly from the leftward translation of the indexing slide 43 or from the translation of an interposer, the consequence of such rockable inclination of the pawls 45 is to effectuate their coupling with the leftwardly adjoining pinions 21, as shown in FIG. 2A, such coupling consisting of the interposition of the upper extremity of each of the inclined pawls between adjoining pairs of projections 21F disposed on the right-side surface of the adjacent higher order pinion.

An interposer 47 is also floatingly disposed between the highest order pawl 45 and an offset projection 51A of the automatic one slide 51, as shown in FIG. 2. The slide 51 is also provided with an offset projection 51B which cooperates with the lowest order pawl 45, the latter pawl being permanently disposed in a fully indexed position and being also rockingly couplable with the lowest order pinion 21 during a runthrough carry, such carry for example serving to transfer all of the pinions from a nine state to a zero state. The slopes 41A formed in the left-hand portion of the internal shaft 41 are effective, during the return translation of the shaft 41 and the indexing slide 43, to translatably restore the pawls 45 (with the exception of the lowest order pawl) to their respective uppermost positions, after they have been rockably restored to their upright positions by means of the partitions of the indexing slide 43 and the interposers 47 jointly housed with said pawls.

Means shown in FIG. 1A and 1B are provided for rotating the shaft 23 a 36 or equivalent one tooth distance in both a counteraccumulating direction and an accumulating direction relative to the pinions 21. A shaft 53 is connected to suitable motive means of the calculating or business machine into .which the preferred embodiment of the invention is incorporated, such shaft, supported by frame members 35 and 36, being rotatable 360 in a counterclockwise direction (as v viewed in FlG. 1) within the sleeve 55, such rotation being efmembers 36 and 66. The shaft 65 is also provided with an arm 71 and with projections 119, 121, and 123. A stud and roller 73 fixed to the arm 71 is cooperably engaged with an aperture 77A of a lever 77, the latter lever being pivotally supported by a short shaft 75 attached to the frame member 36. An elongated slot 778 formed in the uppermost portion of the lever 77 is cooperably engaged with a stud and roller 79 fixed to an extension 81 ofa hub 83 which one end ofthe shaft 23 is fixed. A shaft 111, journaled within the frame members 35 and 36, is rotatably a predetermined distance in either a clockwise or counterclockwise direction depending upon the additive or subtractive nature of the operation selectively indexed through conventional machine means. The shaft 111, and a cutaway cam 117 fixed to the leftmost extremity thereof, are rotated a predetermined distance in a counterclockwise direction (as viewed in FlG. 1) whenever an additive accumulation has been indexed by said conventional means, and are rotated an equivalent distance in a clockwise direction when a subtractive accumulation is indexed. The counterclockwise rotation of the cam 117 is effective, through its cooperation with the projection 121, to translate the shaft 65 to the left to thereby align the projections 67 and 69 with the cams 57 and 59, respectively, as shown in FIG. 1A and the clockwise rotation of the cam 117 is effective, through its cooperation with the projection 119, to translate the shaft 65 to the right to thereby align the projections 67 and 69 with the earns 61 and 63, respectively, as shown in FIG. 1B. As the shaft 53 is rotated said 360 in a counterclockwise direction, during an accumulating operation in which the projections 67 and 69 are aligned with the earns 57 and 59, the shaft 65 is initially rotated a predetermined distance in a counterclockwise direction by the cam 57 acting on the projection 67, and later rotated an equivalent distance in a clockwise direction by the cam 59 acting on the projection 69. Such rotation of the shaft 53, with the projections 67 and 69 aligned with the cams 61 and 63, results inan initial clockwise rotation of the shaft 65, as produced by the action of the cam 63 on the projection 69, followed by an equivalent counterclockwise rotation of the shaft 65, as produced by the action of the cam 61 on the projection 67. Such variable rotation of the shaft 65, as motivated by the earns 57 and 59, or the earns 61 and 63, is translated into a corresponding 36 rotation of the shaft 23 through the cooperating effect of the arm 71, the stud and roller 73, the lever 77, the stud and roller 79 and the arm 81 of the hub 83.

Means are also provided, as shown in H6. 1, for translating the internal shaft 41 and the indexing slide 43 in both a leftward and a rightward direction, at appropriate points in a tens transfer operation. A pair of differently contoured cams 85 and 87 are fixed to the shaft 53 in the proximity of its rightmost extremity, such cams being disposed in cooperating relationship with a pair of rollers 91 of a pivot block 89 which is pivotally attached to the support member 97 by means of a screw stud 95. An upper cylindrical extension 93 of the pivot block 89 is cooperably disposed between a pair of discs 99 which are fixed to the outermost extremtiy of the shaft 41. A yielding connection between the shaft 41 and the rightmast extremity of the indexing slide 43 is provided by means of a retainer nut 101 fixed to the slide 43 and a spring 103 disposed between the nut 101 and the outermost disc 99 as shown in FIG. 2A. At a predetermined point in the counterclockwise rotation of the shaft 53, the internal shaft 41 and the indexing slide 43 are translated predetermined distances to the left by the counterclockwise rotation of the pivot block 89, such rotation being effectuated by the pivoting effect of the cams 85 and 87 on the rollers 91, said translation of the slide 43 being effective to rockably incline the depressibly activated pawls 45 as previously described. At a predetermined later point in the counterclockwise rotation of the shaft 53, the shaft 41 and the indexing slide 43 are translated a predetermined distance to the right by the clockwise rotation of the pivot block 89, such clockwise rotation being effectuated also by the pivoting effect of the cams 85 and 87 on the rollers 91, said translation of the slide 43 being effective to rockably restore the inclined pawls 45 to their upright positions by means of the partitions of the slide 43 and the interposers 47 jointly housed with said pawls, and said translation of the shaft 41 being effective to translatably restore the depressibly activated pawls to their uppermost positions by means of the slopes 41A, as previously described. At still a later point in the rotation of the shaft 53, the shaft 41 is translated a minimal distance to the left by the pivoting effect of the cams 85 and 87 on the pivot block 89, such minimal leftward translation of the shaft 41 being effective to so position the slopes 41A, shown in FIGS. 2 and 2A, that they will not interfere with the depressible indexing of the pawls during a subsequent accumulating operation. This latter minimal translation of the shaft 41 is effectuated independently of the slide 43, such slide being retained in its rightmost home position through the sustained bias of the spring 103 against the retainer nut 101.

The preferred embodiment of the invention, as shown in FIGS. 1 and 13, provides for the use of rotary-type accumulating actuators 113, and for intermediate actuators 115 which are rotationally supported on the sleeve 55. The pinions 21 are engaged with the rotary actuators 113 during the additive entry of amounts therein, and engaged with the intermediate actuators 115 during the substractive entry of amounts, the intermediate actuators 115 being retained in engaged relationship with the rotary actuators 113 as shown in FIG. 13. Means are accordingly provided for selectively engaging the pinions 21 with the rotary actuators 113 or with the intermediate actuators 115, depending upon the add or subtract nature of the selectively indexed accumulating operation. The shaft 111, which was described in connection with the translation of the shaft 65, is provided with a pair of fixed gears 107 and 109 disposed on the rightmost extremity thereof, and provided also with two sets ofcams 125 and a pair of cams 127 (FIGS. 1 and 1C) fixed thereto in spaced-apart relationship, each of said sets of cams I25 and 127 being disposed in cooperating relationship with a pair of offset projections 31 and an arcuate aperture 33 associated with each of the movable frame members 29, each of the arcuate apertures 33 having an upper and lower camming surface cooperable with its associated cam 127. A toothed yoke 105 is activatable upwardly and downwardly by conventional machine means, according to whether an additive or subtractive operation is selectively indexed, such yoke being activated rearwardly (as viewed in FIG. 1) during each accumulating operation. The uppermost teeth of the toothed yoke 105 are engaged with the gear 107 during an add operation, and the lower teeth thereof are engaged with the gear 109 during a subtract operation. It therefore follows that, during an add operation, the shaft 111 is rotated in a counterclockwise direction as viewed in FIG. 1, whereupon the cams 125 cooperate with the rearmost offset projections 31 of the movable frame members 29, to effectively rotate the frame members in a clockwise direction on the sleeve 55, such rotation resulting in the engagement of the pinions 21 with the rotary actuators 113, as best illustrated in FIG. 13. Since the actuators 113 are rotated a differential counterclockwise distance during each additive and subtractive accumulating operation, the engagement of the pinions 21 therewith, during an additive accumulation, results in a clockwise rotation of the pinions 21 during such entry. On the other hand, when a subtractive accumulation is performed, the shaft 111 is rotated in a clockwise direction by the gear 109, whereupon the cams 127 are withdrawn from the upper surfaces of their respective arcuate apertures 33 and cammingly applied against the lower surfaces thereof to effectively translate the latter frame members downwardly on the sleeve 55, such translation resulting in the engagement of the pinions 21 with the intermediate actuators 115 (as also best illustrated in FIG. 13). The pinions 21 are accordingly rotated in a counterclockwise direction during a subtractive accumulation, as the rotary actuators 113 are rotated counterclockwise.

As previously described, the cutaway cam 117 fixed to the leftmost extremity of the shaft 111 is effective for selectively positioning the shaft 65 and the projections 67 and 69 thereof relative to the earns 57, 59, 61 and 63. The counterclockwise rotation of the shaft 111, during an add operation, is effective to translate the shaft 65 to the left (as shown in FIG. 1A),

through the action of the cam 117 against the projection 121. This leftward translation of the shaft 65 is effective to align the projection 67 with the cam 57 and to align the projection 69 with the cam 59. With the projections so aligned, the counterclockwise rotation of the shaft 53 effectuates an initial counterclockwise rotation of the shafts 65 and 23 by means of the cam 59 and the projection 69, followed by a clockwise rotation of these shafts. The clockwise rotation of the shaft 111, during a subtract operation, is effective to translate the shaft 65 to the right (as shown in FIG. 1B), through the action of the cam 117 against the projection 119. This rightward translation of the shaft 65 is effective to align the projection 67 with the cam 61, and to align the projection 69 with the cam 63. With the projections so aligned, the counterclockwise rotation of the shaft 53 cffectuates an initial clockwise rotation of the shafts 65 and 23 by means of the cam 63 and the projection 69, followed by a counterclockwise rotation of these shafts by means of the cam 63 and the projection 69. In both instances the initial rotation of the shafts 65 and 23 corresponds to the counteraccumulating rotation of the pinions 21, and the sub sequent rotation of the shafts 65 and 23 corresponds to the accumulating rotation of the pinions, as determined by the engagement of the pinions with either the rotary actuators 113 or the intermediate actuators 115.

GENERAL OPERATION A brief description is set forth in the following paragraphs to more specifically disclose how a tens transfer operation is performed by the preferred embodiment of the invention.

The pinions 21 are engaged with the rotary actuators 113 or the intermediate actuators (FIG. 1) depending upon the add or subtract nature of the selectively indexed accumulating operation, such engagement being effectuated by the initial rotation of the shaft 111 and the resulting rotation or translation of the movable frame members 29 on the sleeve 55.

The pinions 21 are rotated in a counterclockwise or clockwise accumulating direction by the actuators 113 or 115. When, during this rotation, one or more pinions are rotated from their nine to their zero positions, the wedge-shaped camming surfaces 21D (FIG. 5) of such pinions act on the upper extremities of their associated pawls 45 (FIG. 2) to thereby depressibly activate such pawls to their intermediate positions in the anchor strip 49 (as shown in FIG. 9).

The pinions are then disengaged from the actuators 113 or 115 and engaged with the finger springs 39 of the detent bail 37, such disengagement being effectuated by the return rotation of the shaft 111 (FIG. 1) and the return rotation or translation of the movable frame members 29 on the sleeve 55.

The hollow shaft 23, including the internal shaft 41, the indexing slide 43 and the anchor strip 49, which are keyed therewithin as best illustrated in FIG. 7, are then rotated 36 in either a clockwise or counterclockwise counteraccumulating direction through the rotation of the shaft 53 (FIG. 1) and the above-described action of the earns 57, 59, 61 or 63 on the projections 69 or 67, as influenced by the initial direction of rotation of the shaft 111. During this rotation of the shaft 23, those pawls 45 which were depressibly activated to their intermediate positions by the wedge-shaped camming surfaces of their associated pinions, are further depressibly activated to their fully indexed positions (as shown in FIG. 10) by the action of the camming surfaces 21E of their associated pinions on the studs 45A of the pawls. During this rotation of the shaft 23, also, those pawls 45 which are associated with pinions located in their 9 positions are depressibly activated to their intermediate positions (as shown in FIG. 11) by the action of the wedge-shaped camming surfaces 21D of their associated pinions against the upper extremities of the pawls. In the case of a runthrough carry, this 36 rotation of the shaft 23 is effective to fully index the pawl 45 which is indexibly associated with the lowest order pinion, and effective also to depressibly activate each of the leftwardly adjoining pawls 45 to their partially indexed positions, inasmuch as a runthrough carry is produced by the entry of a digit value of one into the lowest order pinion of an accumulator the individual pinions of which are located in their respective 9 positions.

The internal shaft 41 and indexing slide 43 are then translated predetermined distances to the left through the continued rotation of the shaft 53 (FIG. 1) and the pivoting effect of the earns 85 and 87 on the pivot block 89. This leftward translation of the shaft 41 and the slide 43 is effective to rockably incline those pawls 45 which have been depressibly activated to their fully indexed positions, by means of the partitions of the slide 43 acting upon the projections 45B of the pawls, and effective also to rockably incline one or more pawls which leftwardly adjoin a fully indexed pawl and which themselves have been depressibly activated to their intermediate positions (as shown in FIG. 12), by means of the leftward translation of their rightwardly adjoining interposers 47. The rockably inclined pawls are thereby coupled between adjoining projections 21F (FIG. 6) of their adjacent higher order pinions.

In the case of a runthrough carry, wherein all pinions to the left of the lowest ofder pinions are set to their nine positions, the leftward translation of the indexing slide 43 is effective to rockably incline the pawl indexably associated with the lowest order pinion, such pawl having been fully indexed, to thereby effectuate the leftward translation of the interposer 47 jointly housed therewith in an aperture of such slide, the translation of this interposer being effective to successively incline each of the higher order partially indexed pawls by means of their rightwardly adjacent interposers. As the highest order pawl 45 is so inclined, the interposer 47 jointly housed therewith in an aperture of the slide 43 is translated to the left to thereby effectuate the leftward translation of the automatic one slide 51 by means of the projection 51A. This translation of the automatic one slide serves to rockably incline the rightmost pawl 45 (which is permanently disposed in a fully indexed position) into coupled relationship with the lowest order pinion, by means of the projection 518.

The shaft 23, including the internal shaft 41, the indexing slide 43, the anchor strip 49, and the pawls 45, are then rotated 36 in a clockwise or counterclockwise accumulating direction through the rotation of the shaft 53 (FIG. 1) and the above-described action of the cams 57, 59, 61 or 63 on the projections 69 or 67, as influenced by the initial direction of rotation of the shaft 111. This 36 rotation of the pawls 45 in an accumulating direction is effective to advance those pinions which are coupled with their rightwardly adjoining inclined pawls a one-tooth distance in an accumulating direction.

The internal shaft 41 and indexing slide 43 are then translated a predetermined distance in a rightward return direction through the continued rotation of the shaft 53 and the reverse pivoting effect of the earns 85 and 87 on the pivot block 89. This rightward return translation of the shaft 41 and the index ing slide 43 is efi'ective to rockably restore the inclined and coupled pawls 45 to their upright positions, by means of the partitions of the slide 43 acting on the interposers 47, and to translatably restore the depressibly activated pawls to their uppermost positions, by means of the slopes 41A FIGS. 2 and 2A) of the shaft 41. The initial leftward and rightward return translations of the indexing slide 43 are both effectuated by means of the yielding connection formed by the retainer nut 101 fixed to rightmost extremity of the slide 43 and the spring 103 disposed between the retainer nut and the rightmost disc 99 fixed to the shaft 41, such yielding connection serving to correspondingly activate the slide 43 as the internal shaft 41 is translatably activated by the pivoting effect of the earns 85 and 87 on the pivot block 89.

The internal shaft 41 is then translated a predetermined minimal distance to the left as the shaft 53 completes its 360 counterclockwise rotation, such minimal leftward translation being effective to move the slopes 41A to a nonblocking position relative to the pawls 45, such that the pawls may be depressibly activated during a succeeding accumulating operation. This minimal translation of the shaft 41 is effectuated independently of the slide 43, the latter slide being retained in its rightmost position by the bias of the spring 103 acting upon the nut 101 fixed to the slide.

ADDITIVE ACCUMULATION During an additive accumulation, the toothed yoke 105 is initially lowered and then moved rearwardly (as viewed in FIG. 1) through conventional means disposed within the calculator or business machine, such movements being effective to rotate the gear 107 and the shaft 111 a predetermined distance in a counterclockwise direction. The pair of cams fixed to the shaft 111 are thereby rotated in a counterclockwise direction to effectively rotate the frame members 29 in a clockwise direction on the sleeve 55, and the cutaway cam 117 is rotated in a counterclockwise direction to translate the shaft 65 to the left and to thereby align the projections 67 and 69 with the cams 57 and 59, respectively, as shown in FIG. 1A. The effect of the clockwise rotation of the frame members 29 is to engage the pinions 21 with their corresponding rotary actuators 113, preparatory to the additive entry of theindexed amount.

The indexed amount is then transferred to the pinions 21 by the counterclockwise rotation of the rotary actuators 113 and the corresponding clockwise rotation of the pinions. Should this rotation of the pinions result in the further additive advancement of one or more pinions which are located in their plus 9 positions (relative to their respective pawls), their associated pawls will be depressibly activated to their intermediate positions by the camming surfaces 21D (FIG. 5) of the pinions.

The toothed yoke 105 is then restored forwardly to its home position, thereby activating the gear 107 and the shaft 11 l in a clockwise restorational direction to rotate the movable frame members 29 in a counterclockwise direction on the sleeves 55, such rotation being effectuated by the action of the cams 125 against the foremost offset projections 31. The pinions 21 are accordingly disengaged from the rotary actuators 113 and engaged with the finger springs 39 of the detent bail 37.

The shaft 23 and the pawls 45 are then rotated 36 in a counterclockwise direction relative to the stationary pinions 21, by the counterclockwise rotation of the shaft 53 and the action of the cam 57 on the projection 67, the shaft 23 being accordingly rotated through the rotation of the shaft 65, arm 71, and lever 77. Thiscounterclockwise rotation of the shaft 23 and the pawls 45 relative to the stationary pinions 21 is effective to depressibly activate those pawls which were activated to their intermediate positions during the entry of the indexed amount, to their fully indexed positions, such activation resulting from the camming effect of the leftmost camming surfaces 215 of the stationary pinions (as shown in FIG. 10) on the rotating studs 45A of the pawls. During this counterclockwise rotation of the shaft 23 and the pawls 45, also, those pinions which were located in their plug nine positions after entry of the indexed amount, are depressibly activated to their intermediate positions by the camming effect of the stationary camming surfaces 21D of the pinions on the upper extremities of the rotating pawls.

The internal shaft 41 and the indexing slide 43 are then translated predetermined distances to the left, as previously described, to rockably incline those pawls which have been depressibly activated to their fully indexed positions, and those pawls which Ieftwardly adjoin a fully indexed pawl and which themselves have been depressibly activated to their intermediate positions, such rockable inclining of the pawls serving to effectuate their coupling with their adjacent higher order pinions.

The shaft 23 and the pawls 45 are then rotated 36 in a clockwise direction by the continuing counterclockwise rotation of the shaft 53 and the camming effect of the cam 59 on the projection 69. This clockwise rotation of the shaft 23 is effective to advance those pinions 21 which are coupled with their rightwardly adjoining and rockably inclined pawls a onetooth distance in an accumulating direction.

The internal shaft 41 and the indexing slide 43 are then translated a predetermined distance in a rightward return direction, as previously described, to thereby rockably restore the inclined and coupled pawls to their upright positions, by means of the partitions of the slide 43, and to translatably restore the depressibly activated pawls to their uppermost positions, by means of the slopes 41A formed in the shaft 41.

SUBTRACTIVE ACCUMULATlON During a subtractive accumulation, the toothed yoke 105 is initially raised and then moved rearwardly through conventional means, as previously described, such movements being effective to rotate the gear 109 and the shaft 111 a predetermined distance in a clockwise direction. The pair of cams 127 fixed to the shaft 111 are thereby rotated in a clockwise direction to effectively translate the movable frame members 29 in a downward direction on the sleeve 55, and the cutaway cam 117 in rotating cooperation with the projection 119 serves to translate the shaft 65 to the right to thereby align the projections 67 and 69 of the shaft 65 with the cams 61 and 63, respectively, as shown in FIG. 1B. The effect of the downward translation of the frame members 29 is to engage the pinions 21 with their corresponding intermediate actuators 115, preparatory to the subtractive entry of the indexed amount.

The indexed amount is then transferred to the pinions 21 by the clockwise rotation of the intermediate actuators 115 and the corresponding counterclockwise rotation of the pinions. Should this rotation of the pinions result in the further subtractive advancement of one or more pinions which are located in their minus nine positions, their associated pawls will be depressibly activated to their intermediate positions by the carnming surfaces 21D of the pinions.

The toothed yoke 105 is then restored forwardly to its home position, thereby activating the gear 109 and the shaft 111 in a counterclockwise restorational direction to translate the movable frame members 29 in an upward direction on the sleeve 55. The pinions 21 are accordingly disengaged from the intermediate actuators 115 and engaged with the finger springs 39 of the detent bail 37.

The shaft 23 and the pawls 45 are then rotated 36 in a clockwise direction relative to the stationary pinions 21, by the counterclockwise rotation of the shaft 53 and the action of the cam 68 on the projection 69. This clockwise rotation of the shaft 23 and the pawls 45 relative to the stationary pinions 21 is effective to depressibly activate those pawls which were activated to their intermediate positions during the entry of the indexed amount, to their fully indexed positions, such activation resulting from the carnming effect of the rightmost carnming surfaces 21E of the stationary pinions (as shown in FIG. 5) on the rotating studs 45A of the pawls. During this clockwise rotation of the shaft 23 and the pawls 45, also, those pinions which were located in their minus nine positions after entry of the indexed amount are depressibly activated to their intermediate positions by the carnming effect of the stationary carnming surfaces 21D of the pinions on the upper extremities of the rotation pawls.

The internal shaft 41 and the indexing slide 43 are then translated predetennined distances to the left, as previously described, to rockably incline those pawls which have been depressibly activated to their fully indexed positions, and those pawls which leftwardly adjoin a fully indexed pawl and which themselves have been depressibly activated to their intermediate positions, such rockable inclining of the pawls serving to effectuate their coupling with their adjacent higher order pinions.

The shaft 23 and pawls 45 are then rotated 36 in a counterclockwise direction by the continuing rotation of the shaft 53 and the carnming effect of the cam 61 on the projection 67. This counterclockwise rotation of the shaft is effective to advance those pinions which are coupled with their rightwardly adjoining and rockably inclined pawls a one-tooth distance in a subtractive accumulating direction.

The internal shaft 41 and the indexing slide 43 are then translated a predetermined distance in a rightward return direction, as previously described, to thereby rockably restore the inclined and coupled pawls to their upright positions, and to translatably restore the depressibly activated pawls to their uppermost positions.

It will be observed from the above description of an additive and subtractive accumulation, that the shaft 111 and cutaway cam 117 are rotated in a specified direction in order to selectively engage the pinions with the actuators 113 or 115, and to effectively translate the shaft 65 such that the projections 67 and 69 are properly aligned with the cams 57 and 59, or with the earns 61 and 63, respectively, such translation of the shaft 65 being effectuated by the action of the cutaway cam 117 on the projections 121 or 119. It will also be observed from the above description that the shaft 111 and the cutaway cam 117 are restored to their home positions prior to the time the shaft 23 and pawls 45 are rotated in specified counteraccumulating and accumulating directions by the action of specified ones of the cams 57, 59, 61 and 63 on a specified one of the projections 67 and 69. The projection 123 of the shaft 65, together with a lug formed on the cutaway cam 117, have been provided as a means of retaining the shaft 65 in its selectively translated position after the shaft 111 and cam 117 have been restored to their home positions, the lug of the cam 117 being transversely and blockingly aligned with the projection 123 of the shaft 65 when the cam 117 is so located in its home position, as illustrated in FIGS. 1A and 18.

While the invention has been described with respect to a preferred embodiment thereof, it will be understood that the invention and its various features are capable of changes and variations which lie within the spirit and scope of the following claims. In particular, although the preferred embodiment discloses an accumulator the pinions of which are rotated in an additive and subtractive direction by means of rotary actuators, other well known means may be employed for this purpose without affecting the gist or significance of the invention, such invention being especially concerned with means for producing tens transfers irrespective of the means chosen for entering amounts in the accumulating pinions.

What we claim is:

1. in a calculating machine accumulator having a plurality of ordinally arranged pinions rotatably supported on a pinionbearing first shaft, an improved tens transfer device wherein the transfer of carries to higher order pinions is accomplished by the reciprocal rotationof the pinion-bearing first shaft a one-unit distance relative to the pinions, said device comprismg:

a. a plurality of pawls associated with said plurality of pinions, said pawls being end-anchored within said pinion-bearing first shaft and extending outwardly from apertures formed therein,

b. means associated with said calculator for reciprocally rotating said pinion-bearing first shaft said one-unit distance relative to said pinions,

c. means associated with said accumulator and with said reciprocal rotating means for depressibly indexing said pawls, and

d. means for selectively and translatably inclining predetermined ones of said depressibly indexed pawls to thereby effectuate their coupling with their respective higher order pinions, said coupled pinions being accordingly advanced a one-unit distance during the completion of said reciprocal rotation of said pinion-bearing first shaft relative to said pinions.

2. The tens transfer device defined in claim 1 wherein each of said pawls is end-anchored in an aperture formed in a stationary anchor strip, said end-anchoring being such that each pawl may be depressibly activated by said means for depressibly indexing said pawls, and rockably activated by said means for selectively and translatably inclining said pawls.

The tens transfer device defined in claim I wherein said means for depressibly indexing said pawls comprises:

a wedge-shaped first camming surface arranged on each of said plurality of pinions, each of said camming surfaces being effective to depressibly index its associated pawl to an intermediate indexed position when an exceed-capacity condition occurs in its associated pinion during the accumulation of amounts in said accumulator, and when its associated pinion is disposed in its full-capacity position during said reciprocal rotation of said pinion-bearing first shaft relative to said pinions, and

a pair of second camming surfaces arranged on each of said plurality of pinions, a predetermined one of said second camming surfaces being effective to depressibly index its associated pawl to a fully indexed position when, during said reciprocal rotation of said pinion-bearing first shaft relative to said pinions, said pawl is disposed in its said intermediately indexed position.

The tens transfer device defined in claim 2 wherein said means for selectively and translatably inclining predetermined ones of said depressibly indexed pawls comprises:

. a second shaftresiliently coupled to said apertured slide,

said second shaft having a plurality of slopes disposed below and associated with said plurality of end-anchored pawls, and

translating means associated with said calculator and effectivefor reciprocally translating said resiliently coupled apertured slide and said second shaft, said translation of said slide and said second shaft in a first direction being effective to rockably incline said predetermined ones of said depressibly indexed pawls by means of said partitions or said interposers, and said translation of said slide and said second shaft in a second direction being effective to restore said inclined pawls and said depressibly indexed pawls to their home positions by means of said partitions and said slopes.

. The tens transfer device defined in claim 4 wherein:

6. An improved tens transfer device operatively associated with an accumulator having a plurality of rotatably supported ordinal pinions, said tens transfer device comprising:

a plurality of pawls each one of which is indexibly associated with an ordinal pinion and couplingly associated with an adjacent higher order pinion,

means effective for selectively indexing said pawls,

means effective for coupling said selectively indexed pawls with their adjacent higher order pinions, and

. pawl-driving means effective for bidirectionally rotating said pawls relative to said pinions and for simultaneously advancing said coupled adjacent higher order pinions a one-unit distance in an accumulating direction as said pawls are rotated in a second direction of said bidirectional rotation of said pawls relative to said pinions.

The tens transfer device defined in claim 6 wherein said means for selectively indexing said pawls additionally comprises:

first means responsive to the rotation of said pinions in an accumulating direction and to said pawl-driving means as said pawls are driven in a first direction of said bidirectional rotation of said pawls relative to said pinions, said first means being effective for partially indexing those pawls which are indexibly associated with pinions that are disposed in or rotated past their full capacity positions, and

b. second means responsive to said pawl-driving means as said pawls are driven in said first direction relative to said pinions, said second means being effective for fully indexing said pawls which were partially indexed by said first means during said rotation of said pinions past their full capacity positions.

8. The tens transfer device defined in claim 7 wherein said means for coupling said selectively indexed pawls with their adjacent higher order pinions additionally comprises:

a. translatable means effective for rockably inclining said fully indexed pawls and selected ones of said partially indexed pawls in the direction of their higher order pinions, said selected ones of said partially indexed pawls including those which leftwardly adjoin either a fully indexed pawl or one or more partially indexed pawls which in turn leftwardly adjoin a fully indexed pawl,

b. means associated with each accumulating pinion effective for receiving the pawl which is indexibly associated with the rightwardly adjoining pinion when said pawl is rockably inclined by said translatable means, and

0. means for bidirectionally translating said translatable means, said translation of said latter means in a coupling first direction occurring subsequent to said first direction rotation of said pawls by said pawl-driving means, and said translation of said translatable means in a decoupling second direction occurring subsequent to said second direction rotation of said pawls relative to said pinions.

9. The tens transfer device defined in claim 8 wherein said pawl-driving means effective for bidirectionally rotating said pawls relative to said pinions additionally comprises:

a. a pair of frame members,

b. an apertured shaft rotatably supported by said pair of frame members, said apertured shaft providing rotational support for said rotatably supported pinions,

c. support means disposed within and rotatable with said apertured shaft, said support means providing variable coplanar and angular positioning of said pawls relative to the diameter of said shaft, said apertures of said shaft affording cooperation between said pawls and said means for selectively indexing said pawls and affording cooperation also between said pawls and said means for coupling said selectively indexed pawls with their adjacent higher order pinions, and

d. means for rotating said apertured shaft and said support means a predetermined distance in opposing directions, said distance being equivalent to a one-tooth advancement of said pinions relative to said supporting apertured shaft.

10. The tens transfer device defined in claim 7 wherein said first means for partially indexing said pawls additionally comprises: an inwardly directed wedge-shaped camming surface disposed on the periphery of each of said pinions in cooperating relationship with the outer extremity of its associated pawl, the predetermined adjacent positioning of said camming surface relative to said outer extremity of said pawl denoting the full capacity positioning of said pinion.

11. The tens transfer device defined in claim 8 wherein said second means for fully indexing said pawls which were partially indexed by said first means during said rotation of said pinions past their full capacity positions, additionally comprises:

a. a stud disposed on the side surface of each of said pawls adjacent the pinion with which it is indexibly associated, and

b. at least one angular camming surface disposed on the side surface of each of said pinions adjacent the pawl with which it is indexibly associated, said stud of each of said pawls which were partially indexed by said first means in response to said rotation of said pinions in an accumulating direction being contacted by one of said angular camming surfaces of its associated pinion during said first rotation of said pawls relative to said pinions, to thereby activate said pawls to their fully indexed positions.

12. The tens transfer device defined in claim 11 wherein said means associated with each pinion and effective for receiving the pawl which is indexibly associated with the rightwardly adjoining pinion when said pawl is rockably inclined by said translatable means additionally comprises: a plurality of projections disposed in circular spaced-apart relationship on the side surface of each of said pinions opposite said side surface comprising said angular camming surfaces, said spaced-apart relationship of said projections permitting the coupling interposition of the outermost extremity of said pawl between adjoining pairs of said projections when said pawl is rockably inclined while disposed in either its partially indexed or fully indexed positions.

13. The tens transfer device defined in claim 9 wherein said translatable means effective for rockably inclining said fully indexed pawls and said selected ones of said partially indexed pawls additionally comprises:

a. a translatable shaft disposed within and extending outwardly from at least one extremity of said apertured shaft, said translatable shaft having a plurality of slopes formed by a plurality of cutouts therein, each of said slopes being disposed in contiguous cooperating relationship with the innermost extremity of one of said plurality of pawls,

b. an indexing slide disposed within and extending outwardly from at least one extremity of said apertured shaft, said slide having a plurality of apertures effectively housing said plurality of pawls supported by said support means in said variable coplanar and angular relationship with said diameter of said apertured shaft, and

c. a yieldable connection translatably coupling corresponding extremities of said translatable shaft and said indexing slide extending outwardly from said apertured shaft.

14. The tens transfer device defined in claim 13 wherein said translatable means effective for rockably inclining said fully indexed pawls and said selected ones of said partially indexed pawls additionally comprises:

a. a projection disposed on the side surface of each of said pawls adjacent the pinion with which it is indexibly associated, and

b. an interposer floatably disposed in each of said apertures of said indexing slide leftwardly adjacent said pawl housed by said aperture, said projection of each of said pawls being horizontally aligned with the rightwardly adjacent of said interposers when said pawl is disposed in its partially indexed position, and being horizontally aligned with the rightwardly adjacent partition of the partitions forming said apertures of said indexing slide when said pawl is disposed in its fully indexed position, each of said interposers being effective to rockably incline a partially indexed pawl housed by the leftwardly adjacent aperture of said slide when its rightwardly adjacent and jointly housed pawl is rockably inclined, and each of said partitions of said indexing slide being effective to rockably incline a fully indexed pawl housed by its leftwardly adjacent aperture when said indexing slide is translated by said translatable shaft through said yieldable connection, said rockable inclining of said partially indexed and fully indexed pawls being effectuated through contact of said interposers and said partitions of said slide with said projections of said pawls.

15. The tens transfer device defined in claim 14 and additionally comprising:

a. a first pawl couplingly associated with the lowest order pinion, said first pawl being permanently disposed in said support means in a fully indexed position,

b. a second pawl indexibly associated with the highest order pinion, said second pawl being activatable to a partially indexed position and to a fully indexed position, respectively, in response to said first means and said second means of said means for selectively indexing said pawls, and

c. a translatable slide disposed within said apertured shaft, said slide being translatably responsive to the roekable inclining of said second pawl to effectively incline said first pawl and to thereby couple said lowest order pinion to said apertured shaft for the one-tooth advancement of said pinion in an accumulating direction during said second direction rotation of said pawls relative to said pinions, said translation of said translatable slide being effectuated by the translation of said interposer jointly housed with said second pawl in a corresponding aperture of said indexing slide as said second pawl is rockably inclined by said translatable means.

16. The tens transfer device defined in claim 14 wherein said means for bidirectionally translating said translatable means additionally comprises:

a. a pair of discs fixed in spaced-apart relationship to a portion of said translatable shaft extending outwardly from said apertured shaft,

b. a rotatably mounted pivot block disposed in cooperating relationship with said pair of discs, said pivot block having at least two rollers rotatably disposed on the lower surface thereof,

. a drive shaft associated with and responsive to the cycling of said accumulator, said drive shaft being rotatable one complete revolution in a predetermined direction during each of said cycling operations, and

d. a first pair of cams fixed to said drive shaft in contiguous cooperating relationship with said rollers of said pivot block, said complete revolution of said drive shaft and said cams in said predetermined direction being effective to translate said translatable shaft and said yieldably connected indexing slide in said coupling first and said decoupling second directions, said translation of said indexing slide in said coupling first direction being effective to rockably incline those pawls disposed in their fully indexed positions by means of said partitions, and effective also to rockably incline selected ones of those pawls disposed in their partially indexed positions by means of said interposers, said translation of said translatable shaft and said indexing slide in said decoupling second direction being effective to rockably return said inclined pawls to their coplanar positions relative to the diameter of said apertured shaft by means of said partitions and said interposers, and effective also to translatably return said fully and partially indexed pawls to their restored coplanar positions relative to said diameter of said apertured shaft by means of said slopes, said translation of said translatable shaft and said indexing slide in said decoupling second direction being succeeded by a minimal predetermined translation of said translatable shaft in a direction corresponding to said coupling first direction, said minimal translation being effective to return said slopes to a position where they will not interfere with the full or partial indexing of said pawls during a succeeding operation of said accumulator.

17. The tens transfer device defined in claim 16 wherein said means for rotating said apertured shaft and said support means a predetermined distance in opposing directions additionally comprises:

a. at least a second pair of cams fixed to said drive shaft,

b. a rotatable shaft having a pair of oppositely directed cam follower projections fixed thereto, said shaft being rotatably mounted in parallel relationship with said drive shaft and with said cam follower projections disposed in contiguous cooperating relationship with said second pair of cams,

c. a hub member fixed to one end of said apertured shaft,

and

d. linkage means operably connecting said rotatable shaft to said hub member, said second pair of cams cooperating with said pair of cam follower projections during said complete revolution of said drive shaft to effectively rotate said apertured shaft and said plurality of pawls supported therein in said first and said second directions relative to said pinions, said rotation in said first direction corresponding to the counteraccumulating rotation of said pinions and said rotation in said second direction corresponding to the accumulating rotation of said pinions, said rotation in said counteraccumulating direction being effective to fully index those pawls which were partially indexed in response to said rotation of said pinions past their full capacity positions, and to partially index those pawls indexibly associated with pinions disposed in their full capacity positions, said rotation in said accumulating direction being effective to advance said pinions which are coupled to said apertured shaft by said inclined pawls said one tooth distance in an accumulating direction.

18. An accumulator for use in a calculating machine having a frame, motive means, control means, and a plurality of rotary actuators responsive to said motive means and said control means and effective for entering amounts in said accumulator, said rotary actuators each comprising a driving first and a driven second gear, said accumulator comprising:

a rotatably mounted hollow apertured shaft,

a plurality of ordinally arranged pinions rotatably supported by said hollow apertured shaft,

means for engaging and disengaging said pinions with and from said rotary actuators and for selectively engaging said pinions .with said actuators such that said pinions may be advanced a differential distance in either an additive or subtractive direction in keeping with the values of the amounts entered, and

. tens transfer means substantially disposed within said hollow apertured shaft, said tens transfer means being effective for simultaneously advancing one or more higher order pinions a one-unit distance when one or more adjacent lower order pinions are accumulatively rotated past their full capacity positions.

a first shaft rotatably supported by said machine frame,

b. means responsive to said motive means and said control means for rotating said first shaft a predetermined distance in.either a first or second direction according to the add or subtract nature of the operation indexed, said means being effective also for returning said first shaft to its home position following said rotation in said first or said second direction,

. two pairs of cams fixed to said first shaft in spaced-apart relationship, and

a pair of spaced-apart movable frame members rotatably and translatably mounted on said machine frame, said movable frame members providing rotational support for said hollow apertured shaft, said frame members comprising cam follower means disposed in cooperating relationship with said cams fixed to said first shaft, said rotation of said first shaft in said first direction being effective, through the cooperation of corresponding ones of said pairs of cams and said cam follower means, to rotate said movable frame members in such manner as to engage said pinions with said driving first gears of said rotary actuators, and said rotation of said first shaft in said second direction being effective, through the cooperation of the opposite corresponding ones of said pairs of cams, to translate said movable frame members in such manner as to engage said pinions with said driven second gears of said actuators, said engagement of said pinions with said driving first gears resulting, upon activation of said actuators, in the additive accumulation of an indexed amount in said accumulator, and said engagement of said pinions with said driven second gears resulting in the subtractive accumulation of such amount.

21. The accumulator defined in claim 20 wherein said tens transfer means comprises:

a. an apertured anchor strip disposed within and rotatable with said hollow apertured shaft,

b. a plurality of pawls translatably and rockably supported by said apertures of said anchor strip and extending outwardly through said apertures of said hollow apertured shaft in interposed relationship with adjoining pairs of said pinions, each of said pawls being indexibly associated with its rightwardly adjoining pinion and couplingly associated with its lefwardly adjoining pinion,

c. means for translatably indexing selected ones of said pawls,

d. means for rotating said hollow apertured shaft and said pawls a predetermined distance in a first and a second direction relative to said pinions, said rotation in said first direction being of a counteraccumulating nature and said rotation in said second direction being either of an additive or subtractive accumulating nature depending upon whether an add or subtract operation is indexed,

. means for rockably inclining said translatably indexed pawls in the direction of their adjoining higher order pinions, and

f. means for coupling said rockably inclined pawls with said adjoining higher order pinions, said coupled pinions being thereafter advanced a one-unit distance in either an additive or subtractive accumulating direction as said hollow apertured shaft and said pawls are rotated in said second direction relative to said pinions which are uncoupled.

22. The accumulator defined in claim 2] wherein each of said pinions comprises a ring portion and a toothed portion, said ring portion being indexibly associated with the leftwardly adjacent pawl as said pinion is rotated by its associated rotary actuator, said toothed portion being separately engageable with said driving first and said driven second gears of its associated rotary actuator and engageable also with said detent means, said toothed portion being indexibly associated also with its leftwardly adjacent pawl as said hollow apertured shaft and said pawls are rotated in said first direction relative to said pinions by said means for rotating said hollow apertured shaft.

23. The accumulator defined in claim 22 wherein said means for translatably indexing selected ones of said pawls comprises:

a. an inwardly directed wedge'shaped camming surface disposed on said ring portion of each of said pinions, said camming surface cooperating with the outermost extremity of the pawl with which it is indexibly associated when said pinion is accumulatively rotated past its fullcapacity position by its associated rotary actuator, to thereby translatably activate said pawl to a partially indexed position,

b. a stud disposed on the side surface of each of said pawls adjacent the pinion with which it is indexibly associated, and

c. a pair of angular camming surfaces disposed on the leftside surface of said toothed portion of each of said pinions adjacent the pawl with which it is indexibly associated, said camming surfaces being arranged in equidistant straddling relationship with said wedgeshaped camming surface of said ring portion, a selected one of said pair of angular camming surfaces cooperating with said stud of said pawl when said hollow apertured shaft and said pawls are rotated in said first direction relative to said pinions, to thereby translatably activate said pawls to a fully indexed position when said pawl at the time of said rotation of said shaft is partially indexed, said rotation of said hollow apertured shaft and said pawls in said first direction being effective also, through the cooperation of said wedge-shaped camming surfaces with said outermost extremities of said pawls, to translatably activate those pawls which are disposed in their full capacity positions to their said partially indexed positions.

24. The accumulator defined in claim 23 wherein said means for rotating said hollow apertured shaft and said pawls in said first and said second directions relative to said pinions comprises:

a. a second shaft rotatably supported by said machine frame and responsive to said motive means and said control means, said second shaft being rotatable a complete revolution in a predetermined direction during each cycling operation of said calculating machine,

b. a first and a second pair of cams fixed to said second shaft,

c. a third shaft rotatably and translatably mounted by means of said machine frame in parallel contiguous relationship with said second shaft, and

d. a pair of oppositely directed projections fixed to said third shaft in cooperating relationship with said first and said second pairs ofcams fixed to said second shaft.

25. The accumulator defined in claim 24 wherein said means for rotating said hollow apertured shaft and said pawls in said first and said second directions relative to said pinions additionally comprises:

a. an arm fixed to said third shaft,

b. a hub snuggly fitted to one end of said hollow apertured shaft, and

c. linkage means connecting said arm of said third shaft and said hub of said hollow apertured shaft, said arm, said linkage means and said hub being effective to rotate said hollow apertured shaft and said pawls in directions corresponding to the directions of rotation of said third shaft as motivated by the action of said first or said second pair of cams on said pair of projections during said revolution of said second shaft by said motive means.

26. The accumulator defined in claim 24 wherein said first pair of cams fixed to said second shaft is effective for producing a first and a second rotation of said hollow apertured shaft in which said second rotation is of an additive accumulating nature and said first rotation is of a corresponding counteraccumulating nature, and said second pair of cams fixed to said second shaft is effective for producing a first and a second rotation of said hollow apertured shaft in which said second rotation is of a subtractive accumulating nature and said first rotation is ofa corresponding counteraccumulating nature.

27. The accumulator defined in claim 25 wherein said means for rotating said hollow apertured shaft and said pawls in said first and said second directions relative to said pinions additionally comprises: cam selection means responsive to said rotation of said first shaft in said first or said second directions as saidpinions are selectively engaged with said driving first or said driven second gears of said rotary actuators, said cam selection means being effective for selectively aligning said first or said second pair of cams fixed to said second shaft with said pair of projections fixed to said third shaft, said selective alignment being effectuated by the translation of said third shaft.

28. The accumulator defined in claim 27 wherein said cam selection means comprises:

a. a cutaway cam fixed to said first shaft in contiguous relationship with said linkage means connecting said arm of said third shaft and said hub of said hollow apertured shaft,

b. a first and a second abutment fixed to said third shaft in straddling relationship with said cutaway cam fixed to said first shaft, and

c. a third abutment fixed to said third shaft intermediate said first and said second abutments, said rotation of said first shaft and said cutaway cam in said first direction being effective, through the action of said cutaway cam on said first abutment, to translatably position said third shaft for an additive accumulation wherein said first pair of cams fixed to said second shaft are cooperably aligned with said pair of projections fixed to said third shaft, and said rotation of said first shaft and said cutaway cam in said second direction being effective, through the action of said cutaway cam on said second abutment, to translatably position said third shaft for a subtractive accumulation wherein said second pair of cams fixed to said second shaft are cooperably aligned with said pair of pro jections of said third shaft.

29. The accumulator defined in claim 25 wherein said means for rockably inclining said translatably indexed pawls in the direction of their adjoining higher order pinions comprises:

a. a translatable fourth shaft disposed within and extending outwardly from the end of said hollow apertured shaft opposite said end fitted to said hub of said means for rotating said latter shaft, said fourth shaft having a plurality of slopes formed by a plurality ofcutouts therein,

b. an apertured indexing slide disposed within and extending outwardly from said hollow apertured shaft, said fourth shaft and said indexing slide being rotatable with said hollow apertured shaft and with said apertured anchor strip, each of said apertures of said indexing slide being separated by partitions formed therein, each of said apertures serving to house one of said pawls supported by said anchor strip and extending outwardly through a corresponding aperture in said hollow apertured shaft, and

a yieldable connection translatably and effectively coupling corresponding extremities of said fourth shaft and said indexing slide extending outwardly from said hollow apertured shaft.

30. The accumulator defined in claim 29 wherein said means for rockably inclining said translatably indexed pawls in the direction of their higher order pinions additionally comprises:

a. a third pair of cams fixed in spaced-apart relationship to said second shaft,

b. a pivot block rotatably mounted on said machine frame, said pivot block having a pair of rollers disposed along the lower edge thereof in cooperating relationship with said third pair of cams, and

c. a pair of spaced-apart discs fixed to said translatable fourth shaft in cooperating relationship with said pair of rollers of said pivot block, said third pair of cams being effective, during said complete revolution of said second shaft, to translate said fourth shaft and said apertured indexing slide in a coupling first direction and in a decoupling second direction through said pivot block and said pair of discs, said translation in said first direction being effective to rockably incline selected ones of said translatably indexed pawls to their coupled positions relative to said higher order pinions, and said translation in said second direction being effective to rockably return said inclined pawls to their uncoupled positions relative thereto.

31. The accumulator defined in claim 30 v wherein said means for rockably inclining said translatably indexed pawls in the direction of their higher order pinions additionally comprises:

a. a plurality of interposers floatingly disposed in said apertures of said indexing slide, each of said interposers being jointly housed with a rightwardly adjacent pawl in one of said apertures, and

b. a projection disposed on each of said plurality of pawls, on said side surface comprising said stud of said means for translatably indexing said pawls, said projection being horizontally aligned with the rightwardly adjacent partition of said apertured indexing slide when said pawl is located in its said fully indexed position, and being horizontally aligned with its rightwardly adjacent interposer when said pawl is located in its said partially indexed position, said translation of said apertured indexing slide in said coupling first direction being effective to rockably incline said fully indexed pawls through contact 

1. In a calculating machine accumulator having a plurality of ordinally arranged pinions rotatably supported on a pinionbearing first shaft, an improved tens transfer device wherein the transfer of carries to higher order pinions is accomplished by the reciprocal rotation of the pinion-bearing first shaft a oneunit distance relative to the pinions, said device comprising: a. a plurality of pawls associated with said plurality of pinions, said pawls being end-anchored within said pinionbearing first shaft and extending outwardly from apertures formed therein, b. means associated with said calculator for reciprocally rotating said pinion-bearing first shaft said one-unit distance relative to said pinions, c. means associated with said accumulator and with said reciprocal rotating means for depressibly indexing said pawls, and d. means for selectively and translatably inclining predetermined ones of said depressibly indexed pawls to thereby effectuate their coupling with their respective higher order pinions, said coupled pinions being accordingly advanced a oneunit distance during the completion of said reciprocal rotation of said pinion-bearing first shaft relative to said pinions.
 2. The tens transfer device defined in claim 1 wherein each of said pawls is end-anchored in aN aperture formed in a stationary anchor strip, said end-anchoring being such that each pawl may be depressibly activated by said means for depressibly indexing said pawls, and rockably activated by said means for selectively and translatably inclining said pawls.
 3. The tens transfer device defined in claim 1 wherein said means for depressibly indexing said pawls comprises: a. a wedge-shaped first camming surface arranged on each of said plurality of pinions, each of said camming surfaces being effective to depressibly index its associated pawl to an intermediate indexed position when an exceed-capacity condition occurs in its associated pinion during the accumulation of amounts in said accumulator, and when its associated pinion is disposed in its full-capacity position during said reciprocal rotation of said pinion-bearing first shaft relative to said pinions, and b. a pair of second camming surfaces arranged on each of said plurality of pinions, a predetermined one of said second camming surfaces being effective to depressibly index its associated pawl to a fully indexed position when, during said reciprocal rotation of said pinion-bearing first shaft relative to said pinions, said pawl is disposed in its said intermediately indexed position.
 4. The tens transfer device defined in claim 2 wherein said means for selectively and translatably inclining predetermined ones of said depressibly indexed pawls comprises: a. an apertured slide having a plurality of compartments formed by a plurality of equally spaced partitions, each of said compartments serving to house one of said pawls and a translatable floating interposer, said interposer being disposed to the left of its said jointly housed pawl, b. a second shaft resiliently coupled to said apertured slide, said second shaft having a plurality of slopes disposed below and associated with said plurality of end-anchored pawls, and c. translating means associated with said calculator and effective for reciprocally translating said resiliently coupled apertured slide and said second shaft, said translation of said slide and said second shaft in a first direction being effective to rockably incline said predetermined ones of said depressibly indexed pawls by means of said partitions or said interposers, and said translation of said slide and said second shaft in a second direction being effective to restore said inclined pawls and said depressibly indexed pawls to their home positions by means of said partitions and said slopes.
 5. The tens transfer device defined in claim 4 wherein: a. said stationary anchor strip is interposed between said resiliently coupled apertured slide and said second shaft of said means for selectively and translatably inclining said pawls, and b. said anchor strip and at least a portion of said apertured slide and said second shaft are disposed within said pinion-bearing first shaft.
 6. An improved tens transfer device operatively associated with an accumulator having a plurality of rotatably supported ordinal pinions, said tens transfer device comprising: a. a plurality of pawls each one of which is indexibly associated with an ordinal pinion and couplingly associated with an adjacent higher order pinion, b. means effective for selectively indexing said pawls, c. means effective for coupling said selectively indexed pawls with their adjacent higher order pinions, and d. pawl-driving means effective for bidirectionally rotating said pawls relative to said pinions and for simultaneously advancing said coupled adjacent higher order pinions a one-unit distance in an accumulating direction as said pawls are rotated in a second direction of said bidirectional rotation of said pawls relative to said pinions.
 7. The tens transfer device defined in claim 6 wherein said means for selectively indexing said pawls additionally comprises: a. first means responsive to the rotation of said pinions in an accumulating direction and to said pawl-Driving means as said pawls are driven in a first direction of said bidirectional rotation of said pawls relative to said pinions, said first means being effective for partially indexing those pawls which are indexibly associated with pinions that are disposed in or rotated past their full capacity positions, and b. second means responsive to said pawl-driving means as said pawls are driven in said first direction relative to said pinions, said second means being effective for fully indexing said pawls which were partially indexed by said first means during said rotation of said pinions past their full capacity positions.
 8. The tens transfer device defined in claim 7 wherein said means for coupling said selectively indexed pawls with their adjacent higher order pinions additionally comprises: a. translatable means effective for rockably inclining said fully indexed pawls and selected ones of said partially indexed pawls in the direction of their higher order pinions, said selected ones of said partially indexed pawls including those which leftwardly adjoin either a fully indexed pawl or one or more partially indexed pawls which in turn leftwardly adjoin a fully indexed pawl, b. means associated with each accumulating pinion effective for receiving the pawl which is indexibly associated with the rightwardly adjoining pinion when said pawl is rockably inclined by said translatable means, and c. means for bidirectionally translating said translatable means, said translation of said latter means in a coupling first direction occurring subsequent to said first direction rotation of said pawls by said pawl-driving means, and said translation of said translatable means in a decoupling second direction occurring subsequent to said second direction rotation of said pawls relative to said pinions.
 9. The tens transfer device defined in claim 8 wherein said pawl-driving means effective for bidirectionally rotating said pawls relative to said pinions additionally comprises: a. a pair of frame members, b. an apertured shaft rotatably supported by said pair of frame members, said apertured shaft providing rotational support for said rotatably supported pinions, c. support means disposed within and rotatable with said apertured shaft, said support means providing variable coplanar and angular positioning of said pawls relative to the diameter of said shaft, said apertures of said shaft affording cooperation between said pawls and said means for selectively indexing said pawls and affording cooperation also between said pawls and said means for coupling said selectively indexed pawls with their adjacent higher order pinions, and d. means for rotating said apertured shaft and said support means a predetermined distance in opposing directions, said distance being equivalent to a one-tooth advancement of said pinions relative to said supporting apertured shaft.
 10. The tens transfer device defined in claim 7 wherein said first means for partially indexing said pawls additionally comprises: an inwardly directed wedge-shaped camming surface disposed on the periphery of each of said pinions in cooperating relationship with the outer extremity of its associated pawl, the predetermined adjacent positioning of said camming surface relative to said outer extremity of said pawl denoting the full capacity positioning of said pinion.
 11. The tens transfer device defined in claim 8 wherein said second means for fully indexing said pawls which were partially indexed by said first means during said rotation of said pinions past their full capacity positions, additionally comprises: a. a stud disposed on the side surface of each of said pawls adjacent the pinion with which it is indexibly associated, and b. at least one angular camming surface disposed on the side surface of each of said pinions adjacent the pawl with which it is indexibly associated, said stud of each of said pawls which were partially indexed by said first means in response to said rotation of said pinions in an accumulating direction being contacted by one of said angular camming surfaces of its associated pinion during said first rotation of said pawls relative to said pinions, to thereby activate said pawls to their fully indexed positions.
 12. The tens transfer device defined in claim 11 wherein said means associated with each pinion and effective for receiving the pawl which is indexibly associated with the rightwardly adjoining pinion when said pawl is rockably inclined by said translatable means additionally comprises: a plurality of projections disposed in circular spaced-apart relationship on the side surface of each of said pinions opposite said side surface comprising said angular camming surfaces, said spaced-apart relationship of said projections permitting the coupling interposition of the outermost extremity of said pawl between adjoining pairs of said projections when said pawl is rockably inclined while disposed in either its partially indexed or fully indexed positions.
 13. The tens transfer device defined in claim 9 wherein said translatable means effective for rockably inclining said fully indexed pawls and said selected ones of said partially indexed pawls additionally comprises: a. a translatable shaft disposed within and extending outwardly from at least one extremity of said apertured shaft, said translatable shaft having a plurality of slopes formed by a plurality of cutouts therein, each of said slopes being disposed in contiguous cooperating relationship with the innermost extremity of one of said plurality of pawls, b. an indexing slide disposed within and extending outwardly from at least one extremity of said apertured shaft, said slide having a plurality of apertures effectively housing said plurality of pawls supported by said support means in said variable coplanar and angular relationship with said diameter of said apertured shaft, and c. a yieldable connection translatably coupling corresponding extremities of said translatable shaft and said indexing slide extending outwardly from said apertured shaft.
 14. The tens transfer device defined in claim 13 wherein said translatable means effective for rockably inclining said fully indexed pawls and said selected ones of said partially indexed pawls additionally comprises: a. a projection disposed on the side surface of each of said pawls adjacent the pinion with which it is indexibly associated, and b. an interposer floatably disposed in each of said apertures of said indexing slide leftwardly adjacent said pawl housed by said aperture, said projection of each of said pawls being horizontally aligned with the rightwardly adjacent of said interposers when said pawl is disposed in its partially indexed position, and being horizontally aligned with the rightwardly adjacent partition of the partitions forming said apertures of said indexing slide when said pawl is disposed in its fully indexed position, each of said interposers being effective to rockably incline a partially indexed pawl housed by the leftwardly adjacent aperture of said slide when its rightwardly adjacent and jointly housed pawl is rockably inclined, and each of said partitions of said indexing slide being effective to rockably incline a fully indexed pawl housed by its leftwardly adjacent aperture when said indexing slide is translated by said translatable shaft through said yieldable connection, said rockable inclining of said partially indexed and fully indexed pawls being effectuated through contact of said interposers and said partitions of said slide with said projections of said pawls.
 15. The tens transfer device defined in claim 14 and additionally comprising: a. a first pawl couplingly associated with the lowest order pinion, said first pawl being permanently disposed in said support means in a fully indexed position, b. a second pawl indexibly associated with the highest order pinion, said second pawl being activatable to a partially indexEd position and to a fully indexed position, respectively, in response to said first means and said second means of said means for selectively indexing said pawls, and c. a translatable slide disposed within said apertured shaft, said slide being translatably responsive to the rockable inclining of said second pawl to effectively incline said first pawl and to thereby couple said lowest order pinion to said apertured shaft for the one-tooth advancement of said pinion in an accumulating direction during said second direction rotation of said pawls relative to said pinions, said translation of said translatable slide being effectuated by the translation of said interposer jointly housed with said second pawl in a corresponding aperture of said indexing slide as said second pawl is rockably inclined by said translatable means.
 16. The tens transfer device defined in claim 14 wherein said means for bidirectionally translating said translatable means additionally comprises: a. a pair of discs fixed in spaced-apart relationship to a portion of said translatable shaft extending outwardly from said apertured shaft, b. a rotatably mounted pivot block disposed in cooperating relationship with said pair of discs, said pivot block having at least two rollers rotatably disposed on the lower surface thereof, c. a drive shaft associated with and responsive to the cycling of said accumulator, said drive shaft being rotatable one complete revolution in a predetermined direction during each of said cycling operations, and d. a first pair of cams fixed to said drive shaft in contiguous cooperating relationship with said rollers of said pivot block, said complete revolution of said drive shaft and said cams in said predetermined direction being effective to translate said translatable shaft and said yieldably connected indexing slide in said coupling first and said decoupling second directions, said translation of said indexing slide in said coupling first direction being effective to rockably incline those pawls disposed in their fully indexed positions by means of said partitions, and effective also to rockably incline selected ones of those pawls disposed in their partially indexed positions by means of said interposers, said translation of said translatable shaft and said indexing slide in said decoupling second direction being effective to rockably return said inclined pawls to their coplanar positions relative to the diameter of said apertured shaft by means of said partitions and said interposers, and effective also to translatably return said fully and partially indexed pawls to their restored coplanar positions relative to said diameter of said apertured shaft by means of said slopes, said translation of said translatable shaft and said indexing slide in said decoupling second direction being succeeded by a minimal predetermined translation of said translatable shaft in a direction corresponding to said coupling first direction, said minimal translation being effective to return said slopes to a position where they will not interfere with the full or partial indexing of said pawls during a succeeding operation of said accumulator.
 17. The tens transfer device defined in claim 16 wherein said means for rotating said apertured shaft and said support means a predetermined distance in opposing directions additionally comprises: a. at least a second pair of cams fixed to said drive shaft, b. a rotatable shaft having a pair of oppositely directed cam follower projections fixed thereto, said shaft being rotatably mounted in parallel relationship with said drive shaft and with said cam follower projections disposed in contiguous cooperating relationship with said second pair of cams, c. a hub member fixed to one end of said apertured shaft, and d. linkage means operably connecting said rotatable shaft to said hub member, said second pair of cams cooperating with said pair of cam follower projections during said complete revolution of saId drive shaft to effectively rotate said apertured shaft and said plurality of pawls supported therein in said first and said second directions relative to said pinions, said rotation in said first direction corresponding to the counteraccumulating rotation of said pinions and said rotation in said second direction corresponding to the accumulating rotation of said pinions, said rotation in said counteraccumulating direction being effective to fully index those pawls which were partially indexed in response to said rotation of said pinions past their full capacity positions, and to partially index those pawls indexibly associated with pinions disposed in their full capacity positions, said rotation in said accumulating direction being effective to advance said pinions which are coupled to said apertured shaft by said inclined pawls said one tooth distance in an accumulating direction.
 18. An accumulator for use in a calculating machine having a frame, motive means, control means, and a plurality of rotary actuators responsive to said motive means and said control means and effective for entering amounts in said accumulator, said rotary actuators each comprising a driving first and a driven second gear, said accumulator comprising: a. a rotatably mounted hollow apertured shaft, b. a plurality of ordinally arranged pinions rotatably supported by said hollow apertured shaft, c. means for engaging and disengaging said pinions with and from said rotary actuators and for selectively engaging said pinions with said actuators such that said pinions may be advanced a differential distance in either an additive or subtractive direction in keeping with the values of the amounts entered, and d. tens transfer means substantially disposed within said hollow apertured shaft, said tens transfer means being effective for simultaneously advancing one or more higher order pinions a one-unit distance when one or more adjacent lower order pinions are accumulatively rotated past their full capacity positions.
 19. The accumulator defined in claim 18 and additionally comprising detent means fixed to said frame in cooperating relationship with said plurality of pinions, said detent means being effective for holding said pinions in their differentially set positions when said pinions are disengaged from said rotary actuators.
 20. The accumulator defined in claim 19 wherein said means for engaging and disengaging said pinions with and from said rotary actuators comprises: a. a first shaft rotatably supported by said machine frame, b. means responsive to said motive means and said control means for rotating said first shaft a predetermined distance in either a first or second direction according to the add or subtract nature of the operation indexed, said means being effective also for returning said first shaft to its home position following said rotation in said first or said second direction, c. two pairs of cams fixed to said first shaft in spaced-apart relationship, and d. a pair of spaced-apart movable frame members rotatably and translatably mounted on said machine frame, said movable frame members providing rotational support for said hollow apertured shaft, said frame members comprising cam follower means disposed in cooperating relationship with said cams fixed to said first shaft, said rotation of said first shaft in said first direction being effective, through the cooperation of corresponding ones of said pairs of cams and said cam follower means, to rotate said movable frame members in such manner as to engage said pinions with said driving first gears of said rotary actuators, and said rotation of said first shaft in said second direction being effective, through the cooperation of the opposite corresponding ones of said pairs of cams, to translate said movable frame members in such manner as to engage said pinions with said driven second gears of said actuators, said engagement of said pinions with said driving first gears resulting, upoN activation of said actuators, in the additive accumulation of an indexed amount in said accumulator, and said engagement of said pinions with said driven second gears resulting in the subtractive accumulation of such amount.
 21. The accumulator defined in claim 20 wherein said tens transfer means comprises: a. an apertured anchor strip disposed within and rotatable with said hollow apertured shaft, b. a plurality of pawls translatably and rockably supported by said apertures of said anchor strip and extending outwardly through said apertures of said hollow apertured shaft in interposed relationship with adjoining pairs of said pinions, each of said pawls being indexibly associated with its rightwardly adjoining pinion and couplingly associated with its lefwardly adjoining pinion, c. means for translatably indexing selected ones of said pawls, d. means for rotating said hollow apertured shaft and said pawls a predetermined distance in a first and a second direction relative to said pinions, said rotation in said first direction being of a counteraccumulating nature and said rotation in said second direction being either of an additive or subtractive accumulating nature depending upon whether an add or subtract operation is indexed, e. means for rockably inclining said translatably indexed pawls in the direction of their adjoining higher order pinions, and f. means for coupling said rockably inclined pawls with said adjoining higher order pinions, said coupled pinions being thereafter advanced a one-unit distance in either an additive or subtractive accumulating direction as said hollow apertured shaft and said pawls are rotated in said second direction relative to said pinions which are uncoupled.
 22. The accumulator defined in claim 21 wherein each of said pinions comprises a ring portion and a toothed portion, said ring portion being indexibly associated with the leftwardly adjacent pawl as said pinion is rotated by its associated rotary actuator, said toothed portion being separately engageable with said driving first and said driven second gears of its associated rotary actuator and engageable also with said detent means, said toothed portion being indexibly associated also with its leftwardly adjacent pawl as said hollow apertured shaft and said pawls are rotated in said first direction relative to said pinions by said means for rotating said hollow apertured shaft.
 23. The accumulator defined in claim 22 wherein said means for translatably indexing selected ones of said pawls comprises: a. an inwardly directed wedge-shaped camming surface disposed on said ring portion of each of said pinions, said camming surface cooperating with the outermost extremity of the pawl with which it is indexibly associated when said pinion is accumulatively rotated past its full-capacity position by its associated rotary actuator, to thereby translatably activate said pawl to a partially indexed position, b. a stud disposed on the side surface of each of said pawls adjacent the pinion with which it is indexibly associated, and c. a pair of angular camming surfaces disposed on the left-side surface of said toothed portion of each of said pinions adjacent the pawl with which it is indexibly associated, said camming surfaces being arranged in equidistant straddling relationship with said wedge-shaped camming surface of said ring portion, a selected one of said pair of angular camming surfaces cooperating with said stud of said pawl when said hollow apertured shaft and said pawls are rotated in said first direction relative to said pinions, to thereby translatably activate said pawls to a fully indexed position when said pawl at the time of said rotation of said shaft is partially indexed, said rotation of said hollow apertured shaft and said pawls in said first direction being effective also, through the cooperation of said wedge-shaped camming surfaces with said outermost extremities of said pawls, to translatably activate those pAwls which are disposed in their full capacity positions to their said partially indexed positions.
 24. The accumulator defined in claim 23 wherein said means for rotating said hollow apertured shaft and said pawls in said first and said second directions relative to said pinions comprises: a. a second shaft rotatably supported by said machine frame and responsive to said motive means and said control means, said second shaft being rotatable a complete revolution in a predetermined direction during each cycling operation of said calculating machine, b. a first and a second pair of cams fixed to said second shaft, c. a third shaft rotatably and translatably mounted by means of said machine frame in parallel contiguous relationship with said second shaft, and d. a pair of oppositely directed projections fixed to said third shaft in cooperating relationship with said first and said second pairs of cams fixed to said second shaft.
 25. The accumulator defined in claim 24 wherein said means for rotating said hollow apertured shaft and said pawls in said first and said second directions relative to said pinions additionally comprises: a. an arm fixed to said third shaft, b. a hub snuggly fitted to one end of said hollow apertured shaft, and c. linkage means connecting said arm of said third shaft and said hub of said hollow apertured shaft, said arm, said linkage means and said hub being effective to rotate said hollow apertured shaft and said pawls in directions corresponding to the directions of rotation of said third shaft as motivated by the action of said first or said second pair of cams on said pair of projections during said revolution of said second shaft by said motive means.
 26. The accumulator defined in claim 24 wherein said first pair of cams fixed to said second shaft is effective for producing a first and a second rotation of said hollow apertured shaft in which said second rotation is of an additive accumulating nature and said first rotation is of a corresponding counteraccumulating nature, and said second pair of cams fixed to said second shaft is effective for producing a first and a second rotation of said hollow apertured shaft in which said second rotation is of a subtractive accumulating nature and said first rotation is of a corresponding counteraccumulating nature.
 27. The accumulator defined in claim 25 wherein said means for rotating said hollow apertured shaft and said pawls in said first and said second directions relative to said pinions additionally comprises: cam selection means responsive to said rotation of said first shaft in said first or said second directions as said pinions are selectively engaged with said driving first or said driven second gears of said rotary actuators, said cam selection means being effective for selectively aligning said first or said second pair of cams fixed to said second shaft with said pair of projections fixed to said third shaft, said selective alignment being effectuated by the translation of said third shaft.
 28. The accumulator defined in claim 27 wherein said cam selection means comprises: a. a cutaway cam fixed to said first shaft in contiguous relationship with said linkage means connecting said arm of said third shaft and said hub of said hollow apertured shaft, b. a first and a second abutment fixed to said third shaft in straddling relationship with said cutaway cam fixed to said first shaft, and c. a third abutment fixed to said third shaft intermediate said first and said second abutments, said rotation of said first shaft and said cutaway cam in said first direction being effective, through the action of said cutaway cam on said first abutment, to translatably position said third shaft for an additive accumulation wherein said first pair of cams fixed to said second shaft are cooperably aligned with said pair of projections fixed to said third shaft, and said rotation of said first shaft and said cutaway cam in said second directiOn being effective, through the action of said cutaway cam on said second abutment, to translatably position said third shaft for a subtractive accumulation wherein said second pair of cams fixed to said second shaft are cooperably aligned with said pair of projections of said third shaft.
 29. The accumulator defined in claim 25 wherein said means for rockably inclining said translatably indexed pawls in the direction of their adjoining higher order pinions comprises: a. a translatable fourth shaft disposed within and extending outwardly from the end of said hollow apertured shaft opposite said end fitted to said hub of said means for rotating said latter shaft, said fourth shaft having a plurality of slopes formed by a plurality of cutouts therein, b. an apertured indexing slide disposed within and extending outwardly from said hollow apertured shaft, said fourth shaft and said indexing slide being rotatable with said hollow apertured shaft and with said apertured anchor strip, each of said apertures of said indexing slide being separated by partitions formed therein, each of said apertures serving to house one of said pawls supported by said anchor strip and extending outwardly through a corresponding aperture in said hollow apertured shaft, and c. a yieldable connection translatably and effectively coupling corresponding extremities of said fourth shaft and said indexing slide extending outwardly from said hollow apertured shaft.
 30. The accumulator defined in claim 29 wherein said means for rockably inclining said translatably indexed pawls in the direction of their higher order pinions additionally comprises: a. a third pair of cams fixed in spaced-apart relationship to said second shaft, b. a pivot block rotatably mounted on said machine frame, said pivot block having a pair of rollers disposed along the lower edge thereof in cooperating relationship with said third pair of cams, and c. a pair of spaced-apart discs fixed to said translatable fourth shaft in cooperating relationship with said pair of rollers of said pivot block, said third pair of cams being effective, during said complete revolution of said second shaft, to translate said fourth shaft and said apertured indexing slide in a coupling first direction and in a decoupling second direction through said pivot block and said pair of discs, said translation in said first direction being effective to rockably incline selected ones of said translatably indexed pawls to their coupled positions relative to said higher order pinions, and said translation in said second direction being effective to rockably return said inclined pawls to their uncoupled positions relative thereto.
 31. The accumulator defined in claim 30 wherein said means for rockably inclining said translatably indexed pawls in the direction of their higher order pinions additionally comprises: a. a plurality of interposers floatingly disposed in said apertures of said indexing slide, each of said interposers being jointly housed with a rightwardly adjacent pawl in one of said apertures, and b. a projection disposed on each of said plurality of pawls, on said side surface comprising said stud of said means for translatably indexing said pawls, said projection being horizontally aligned with the rightwardly adjacent partition of said apertured indexing slide when said pawl is located in its said fully indexed position, and being horizontally aligned with its rightwardly adjacent interposer when said pawl is located in its said partially indexed position, said translation of said apertured indexing slide in said coupling first direction being effective to rockably incline said fully indexed pawls through contact of said partitions of said indexing slide with said projections of said pawls, and to also rockably incline said partially indexed pawls which leftwardly adjoin said fully indexed pawls through contact of said interposers with said projections, said interposers being translated within their respeCtive apertures of said indexing slide by said rockable inclining of said pawls jointly housed by said apertures, said translation of said indexing slide in said decoupling second direction being effective to rockably return said inclined pawls to their uncoupled home positions relative to said higher order pinions through the return translation of said interposers within their respective apertures of said indexing slide, as motivated by said leftwardly adjacent partitions of said slide, and said translation of said fourth shaft in said decoupling second direction being effective to translatably return said fully indexed pawls and said partially indexed pawls to their home positions through the action of said slopes on said innermost extremities of said pawls. 